CN106767007B - The heat exchanger of pointed structures is set outside a kind of pipe - Google Patents
The heat exchanger of pointed structures is set outside a kind of pipe Download PDFInfo
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- CN106767007B CN106767007B CN201611052038.9A CN201611052038A CN106767007B CN 106767007 B CN106767007 B CN 106767007B CN 201611052038 A CN201611052038 A CN 201611052038A CN 106767007 B CN106767007 B CN 106767007B
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- heat
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- heating surface
- metallic rod
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
Abstract
The invention provides a kind of heat exchanger, the heat exchanger includes tube side side and shell side side, the tube side side includes inlet tube, inlet plenum, heating surface bank, outlet chamber and outlet, and the hot fluid enters inlet plenum from inlet tube, passes sequentially through heating surface bank, outlet chamber and outlet；The shell side side includes intake channel, inner casing, shell and outlet chamber, the cold fluid passes sequentially through space and the outlet chamber that intake channel, inner casing and shell are limited, inlet plenum, heating surface bank, outlet chamber are arranged in the space that inner casing and shell are limited, the metallic rod that the heating surface bank outer wall stretches out, the metal rod ends are pointed structures, and the direction from heating surface bank outer wall to the end of the metallic rod is relative with the flow direction of cold fluid.It is pointed bar that end is set outside heat exchanger tube, can be in the flowing of biphase gas and liquid flow, on the one hand laminar sublayer can be destroyed, increase heat transfer area and carry out augmentation of heat transfer, and because being bar, flow resistance is small, also the flow resistance of shell side will not be increased, and by setting point, can prick a bubble, realize and expand gas-liquid interface and gas phase boundary and strengthen disturbance.
Description
Technical field
The invention belongs to field of heat exchangers, be related to a kind of shell-and-tube heat exchanger, more particularly to a kind of low flow resistance, close-coupled,
Residual heat removal heat exchanger with higher natural-circulation capacity and security.
Background technology
Residual heat removal heat exchanger is the heat exchange hinge of residual heat removal system, is to be related to the important of plurality of devices to set
It is standby, such as the safety of the reactor shutdown in nuclear reaction.At present, Generation Ⅲ and atomic marine plant are generally used
Heat Discharging System of Chinese, further to improve inherent safety, this requires that the flow resistance of Residual heat removal cooler is as far as possible low
To improve natural circulation flow, atomic marine plant also requires that Residual heat removal cooler compact volume is small and arranged with saving heap cabin
Space.Most of existing Residual heat removal cooler is arranged in containment or heap cabin, and residual heat of nuclear core drains into final low-temperature receiver and also needed
To pass through a heat exchange again, the c-type Residual heat removal heat exchanger for the nuclear power technology that such as U.S. AP1000 is used is arranged in containment
In cooling water tank cooling water, cooling water evaporation could be by heat derives containment, some Residual heat removals in the condensation of containment shell wall
Cooler improves runner on the basis of traditional heat exchangers and flow adapts it to natural cycle system, still remains with shell-side, such as
" a kind of natural-circulation heat exchanger for supercritical water reactor Residual heat removal "（The patent No.：ZL201210301144.1）.
Stream-liquid two-phase flow can be formed in the general shell side of afterheat heat exchanger, because the presence of the bubble in stream-liquid two-phase flow, leads
The shell side side coefficient of heat transfer is caused to decline, it is impossible to meet normal Residual heat removal requirement.In view of the above-mentioned problems, the invention provides one kind
New heat exchanger, so that the problem of solving above-mentioned.
The content of the invention
To achieve these goals, technical scheme is as follows：
A kind of heat exchanger, the heat exchanger includes tube side side and shell side side, and the tube side side includes inlet tube, snout cavity
Room, heating surface bank, outlet chamber and outlet, the hot fluid enter inlet plenum from inlet tube, pass sequentially through heating surface bank,
Outlet chamber and outlet；The shell side side includes intake channel, inner casing, shell and outlet chamber, and the cold fluid is led to successively
Cross space and outlet chamber that intake channel, inner casing and shell are limited, it is characterised in that the heating surface bank outer wall stretches out
Metallic rod, the metal rod ends be pointed structures, from direction from heating surface bank outer wall to the end of the metallic rod with it is cold
The flow direction of fluid is relative.
Preferably, the included angle A of the metallic rod and heating surface bank outside wall surface is 30-60 degree.
Preferably, the distance between adjacent tube center of heat-exchanging tube bundle is the 1.7- of heat-exchanging tube bundle outer tube diameter
2.5 times, the pointed structures of the end of metallic rod are apart from the outer tube wall of heat-exchanging tube bundle apart from 0.4-0.6 times that h is outer tube diameter.
Preferably, the metallic rod includes the sloping portion of connection heat-exchanging tube bundle and is connected with sloping portion and with changing
The parallel portion of heat pipe bundle diameter parallel, described tip is arranged on the end of parallel portion.
Preferably, the metallic rod is multiple, the distribution density M of metallic rod is used as the function F apart from intake channel
（S）, i.e. M=F (S), on same heat-exchanging tube bundle, F ' (S)>0, wherein F ' (S) is F（S）First order derivative.
Preferably, F " (S)>(S) is F for 0, wherein F "（S）Second derivative.
Preferably, the metallic rod is multiple, the distribution density M of metallic rod is used as the function F apart from intake channel
（S）, i.e. M=F (S), on same heat-exchanging tube bundle, F ' (S)>0, wherein F ' (S) is F（S）First order derivative.
Preferably, F " (S)>(S) is F for 0, wherein F "（S）Second derivative.
Preferably, function Fs of the distribution density M of metallic rod as height（H）, i.e. M=F (H), F ' (H)>0, wherein F '
(H) it is F（H）First order derivative.
Preferably, F " (H)>(H) is F for 0, wherein F "（H）Second derivative.
Preferably, described inner casing and shell are the inner casing and shell in heap cabin respectively, described hot fluid is that high temperature is anti-
The cooling agent of heap is answered, described cold fluid is cooling water.
Preferably, the exit passageway is higher than the position that intake channel is set, described inlet plenum compares outlet chamber
The position of setting is high.
Preferably, setting orifice plate in exit passageway.
Preferably, described inlet tube and outlet is also disposed at the part that inlet plenum and outlet chamber are connected
In arcuation space.
Preferably, the part that the inlet tube and outlet are connected with inlet plenum and outlet chamber is flexible structure
Or elastic construction.
Preferably, the metallic rod that the heating surface bank outer wall stretches out, the metal rod ends are pointed structures, from
The direction of the end of metallic rod described in heating surface bank outer wall case and the flow direction of cold fluid it is relative.
Compared with prior art, it is of the invention to have the following advantages：
1）Set end to be pointed bar outside heat exchanger tube, on the one hand be able to can be broken in the flowing of biphase gas and liquid flow
Bad laminar sublayer, increase heat transfer area carries out augmentation of heat transfer, and because being bar, flow resistance is small, will not also increase shell side
Flow resistance, and by setting point, can prick a bubble, realize and expand gas-liquid interface and gas phase boundary and strengthen
Disturbance.
2）The heat-exchanging tube bundle of heat exchanger is arcuate structure, and has identical arcuate structure with inner casing and shell, can be with
Freely expanded with heat and contract with cold in the space of inner casing and shell.
3）It is further to improve by setting metallic rod to change along the rule on fluid flow direction and short transverse
Heat transfer effect.
4）Residual heat removal cooler is arranged in containment or heap out of my cabin, is not take up containment or heap cabin arrangement space；
5）Residual heat removal cooler is immersed in cooling water large space, and residual heat of nuclear core is expelled to final low-temperature receiver and only needed to once
Heat exchange, substantially reduces the path of Residual heat removal, improves the speed of response；
6）Residual heat removal cooler is not provided with special shell side housing, but make use of containment or the inner casing in heap cabin and
Interlayer between shell, flow resistance is very low, substantially increases natural-circulation capacity.
7）The height and position of heat exchanger can up and down be adjusted in interlayer, not limited by the interference of other equipment pipeline in heap cabin
System, you can regulation tube side and shell side Cool Hot Core difference in height, so as to realize the natural-circulation capacity and heat-carrying capacity of tube side and shell side
Matching.
Brief description of the drawings
Fig. 1 is low flow resistance close-coupled Residual heat removal cooler schematic diagram；
Fig. 2 is the tangent plane schematic diagram for the heat-exchanging tube bundle for setting metallic rod；
Fig. 3 is the tangent plane schematic diagram for another heat-exchanging tube bundle for setting metallic rod；
Fig. 4 is the tangent plane schematic diagram for the heat exchanger tube for setting inner fin；
Fig. 5 is the floor map of heat-exchanging tube bundle expansion.
In figure：1- inlet tubes；2- inlet plenums；3- heating surface banks；4- outlet chamber；5- outlets；6- intake channels；
7- inner casings；8- shells；9- exit passageways；10- heaps cabin；11- low-temperature receivers.
3-1 metallic rods, 3-1-1 pointed structures, 3-1-2 sloping portions, horizontal component 3-1-3,3-2 inner fin, 3-3 is small logical
Road.
Embodiment
The embodiment to the present invention is described in detail below in conjunction with the accompanying drawings.
Herein, if without specified otherwise, being related to formula, "/" represents division, and "×", " * " represent multiplication.
As shown in figure 1, a kind of heat exchanger, the heat exchanger includes tube side side and shell side side, the tube side side includes import
Pipe 1, inlet plenum 2, heating surface bank 3, outlet chamber 4 and outlet 5, the hot fluid enter inlet plenum 2 from inlet tube 1,
Pass sequentially through heating surface bank 3, outlet chamber 4 and outlet 5；The shell side side includes intake channel 6, inner casing 7, shell 8 and gone out
Mouth passage 9, the cold fluid passes sequentially through space and the exit passageway 9 that intake channel 6, inner casing 7 and shell 8 are limited, snout cavity
Room 2, heating surface bank 3, outlet chamber 4 are arranged in the space that inner casing and shell are limited, and the inner casing 7 and shell 8 are arcuation cloth
Put, the curved arrangement of described heating surface bank 3, arc and inner casing 7, the arc of shell 8 of the heating surface bank 3 have identical
The center of circle.
Set by the arcuation of above-mentioned phase concentric structure, and by inlet plenum 2 and outlet chamber 4 be arranged on inner casing and
In the arcuation space of shell formation, the heating surface bank 3 can in the arcuation space of inner casing and shell formation freely heat expansion
Shrinkage, therefore the applicable temperature range of heat-exchanging tube bundle and liquid scope are more extensive, and the application of heat exchanger has been expanded significantly.
Preferably, described inlet tube 1 and the part being connected with inlet plenum 2 and outlet chamber 4 of outlet 2
It is arranged in arcuation space, and preferably, the inlet tube 1 and outlet 2 are connected with inlet plenum 2 and outlet chamber 4
The part connect is flexible structure or elastic construction.
By setting flexible structure or elastic construction, can further facilitate heat-exchanging tube bundle 3 in arc space from
Stretched by ground.
Preferably, as shown in Fig. 2 metallic rod 3-1, the metallic rod 3-1 that the outer wall of the heating surface bank 3 stretches out
End is pointed structures 3-1-1, from the direction of metallic rod 3-1 end and the flowing of cold fluid described in the outer wall case of heating surface bank 3
Direction is relative.I.e. pointed structures head on against the next cold fluid of stream.The signified flow direction of arrow as shown in Figure 2.
Preferably, as shown in Fig. 2 the included angle A of the metallic rod 3-1 and the outside wall surface of heating surface bank 3 is 30-60 degree, entering
One step is preferably 40-45 degree.
Preferably, as shown in Fig. 2 the distance between adjacent tube center of heat-exchanging tube bundle is that heat-exchanging tube bundle outer tube is straight
1.7-2.5 times of footpath, the pointed structures 3-1-1 of metallic rod 3-1 end is apart from the preferred apart from h of the outer tube wall of heat-exchanging tube bundle 3
For 0.4-0.6 times of outer tube diameter.
Pass through above-mentioned preferred angle and distance so that in the case of resistance is less, realize good heat transfer effect.
The outside of heat exchanger tube 3 sets end to be pointed bar, on the one hand be able to can be destroyed in the flowing of biphase gas and liquid flow
Laminar sublayer, and increase heat transfer area progress augmentation of heat transfer, and also because being bar, flow resistance is small, will not also increase shell side
Flow resistance, and by setting point, the bubble in biphase gas and liquid flow can be punctured, realize expand gas-liquid interface and
Gas phase boundary simultaneously strengthens disturbance.Therefore by setting pointed bar, the coefficient of heat transfer of shell side side is greatly improved.
Preferably, the metallic rod 3-1 is multiple, metallic rod 3-1 distribution density M is as apart from intake channel 6
Function F（S）, i.e. M=F (S), on same heat-exchanging tube bundle, F ' (S)>0, wherein F ' (S) is F（S）First order derivative.That is edge
The flow direction of cold fluid, described metallic rod 3-1 distribution density is increasing.Because along the flow direction of fluid,
The cooling fluid temperature more and more higher of shell side, the gas caused by biphase gas and liquid flow is also more and more, therefore by there is rule
The multiple pointed metallic rod 3-1 of setting of rule, can further improve the coefficient of heat transfer, save material.It is found through experiments that, it is regular
Ground sets metallic rod 3-1 distribution density, by increasing capacitance it is possible to increase 20% or so heat exchange efficiency, and can also reduce by 5% or so stream
Dynamic resistance.
Preferably, F " (S)>(S) is F for 0, wherein F "（S）Second derivative.I.e. along the flow direction of cold fluid,
The amplitude that described metallic rod 3-1 distribution density is increasing constantly increases.Find in an experiment, the growth of gas is not
With the growth apart from line style, and in the growth of increase formula, therefore by setting above-mentioned rule to change, further improve and change
The thermal efficiency.
Preferably, metallic rod 3-1 is also arc structure.By being arranged such, it is ensured that and the flow direction phase of cold fluid
Correspondence, improves flow-disturbing effect.
Preferably, metallic rod 3-1 include connection heat-exchanging tube bundle sloping portion 3-1-2 and with sloping portion 3-1-2 phases
Even and with the parallel portion 3-1-3 of heat-exchanging tube bundle diameter parallel.Described tip 3-1-1 is arranged on parallel portion 3-1-3's
End.
Preferably, described parallel portion 3-1-3 metallic rods are arc structure, the circular arc where parallel portion 3-1-3
It is same with the center of circle where the circular arc of heat-exchanging tube bundle 3.
By setting parallel portion 3-1-3, the flow direction of tip 3-1-1 straight cutting cooling fluids can be made, heat exchange is improved
Effect.
Preferably, as shown in figure 3, the included angle A of the sloping portion 3-1-2 and heat-exchanging tube bundle tube wall is 45-70 degree,
Preferably 55-60 degree.
Pass through above-mentioned preferred angle so that in the case of resistance is less, realize good heat transfer effect.
Preferably, the discharge of residual heat of nuclear core of the described heat exchanger applications in the heap cabin 10 in nuclear reactor.It is described
Inner casing and shell be respectively heap cabin 10 inner casing and shell, described hot fluid is the cooling agent of reactor, the cooling agent
Described cold fluid is cooling water.
Reactor coolant from reactor core, flow successively through the inlet tube 1 of Residual heat removal cooler tube side, the Room of snout cavity 2,
Heating surface bank 3, outlet chamber 4 and outlet 5, after the cooling water cooling in Residual heat removal cooler shell side interlayer, return to heap
Core.Cooling water flows successively through the intake channel 6, inner casing 7 and shell 8 of Residual heat removal cooler shell side from the bottom of low-temperature receiver 11
Interlayer, exit passageway 9 are put into, after the reactor coolant heating of Residual heat removal cooler tube side, low-temperature receiver 11 is flowed upwardly into.
By being arranged in interlayer so that the height and position of heat exchanger can up and down be adjusted in interlayer, not by heap cabin 10
The interference limitation of other equipment pipeline, you can regulation tube side and shell side Cool Hot Core difference in height, thus realize tube side and shell side from
The matching of right circulation ability and heat-carrying capacity.And by being arranged in interlayer, the space in heap cabin 10, waste heat can be made full use of
Discharge cooler shell side make use of mezzanine space between inner casing and shell, not increase extra equipment, pipeline, valve and attached
The structures such as part, the path of whole shell-side flow path is shorter, and section is wider, simple structure, the characteristics of with low flow resistance.
Preferably, the exit passageway 9 is higher than the position that intake channel 6 is set, described inlet plenum 2 compares outlet plenum
The position that room 4 is set is high.By above-mentioned setting, the tube side of heat exchanger and shell side set up natural circulation, constantly
Residual heat of nuclear core in heap cabin is expelled to low-temperature receiver.
Preferably, function Fs of the metallic rod 3-1 distribution density M as height（H）, i.e. M=F (H), F ' (H)>0, its
Middle F ' (H) is F（H）First order derivative.I.e. with the increase of height, described metallic rod 3-1 distribution densities are increasing.Because
With the increase of height, the gas in gas-liquid two-phase is more and more, therefore by increasing metallic rod 3-1 density, can be further
Metallic rod is distributed according to rule, the coefficient of heat transfer is improved.It is found through experiments that, it is possible to increase 15%-18% or so heat transfer coefficients,
But also can further reduce by 3% flow resistance.
Preferably, F " (H)>(H) is F for 0, wherein F "（H）Second derivative.I.e. with the increase of height, described gold
The increasing amplitude of category bar 3-1 distribution densities constantly increases.It is found through experiments that, with the increase of height, the increasing of bubble
Plus be not line style increase, but increasing degree more and more higher, therefore by setting, further improve also hot coefficient.
Preferably, setting orifice plate in exit passageway 9.By setting orifice plate, cool down boiling water when can play stream and
Suppress the effect flow backwards, keep two phase natural circulation flowing stable
Preferably, it is many circular heat exchanger tubes 3 that the heat-exchanging tube bundle, which is cross section,.
As shown in figure 4, the inside of heat exchanger tube 3 sets inner fin 3-2, the inner fin 3-2 to be divided into heat exchanger tube multiple
Passage aisle 3-3, sets intercommunicating pore 3-2-1, so that adjacent passage aisle 3-3 communicates with each other on inner fin.
By setting inner fin 3-2, heat exchanger tube is divided into multiple passage aisle 3-3, further augmentation of heat transfer, but accordingly
The pressure increase of flow of fluid.By setting intercommunicating pore 3-2-1, it is ensured that the connection between adjacent passage aisle 3-3, so that
Fluid in the big passage aisle of pressure can flow into the small passage aisle of neighbouring pressure, and solving the inside of condensation end, each is small
The pressure of runner 26 is uneven and the problem of excessive local pressure, so that abundant flowing of the fluid in heat exchanger channels is promoted,
Simultaneously by the setting of intercommunicating pore, the pressure inside heat exchanger tube is also reduced, heat exchange efficiency is improved.
It is preferred that, along the flow direction of cooling agent, the area of the intercommunicating pore is constantly reduced.
Described intercommunicating pore 3-2-1 is square structure, and along the flow direction of cooling agent, the square length of side is not
Disconnected reduction.
Preferably, the diameter parallel of the square diagonal and heat-exchanging tube bundle.
Along the flow direction of fluid, the fluid in heat exchanger tube is constantly condensed, the gas in biphase gas and liquid flow also by
Gradually be condensed into liquid so that the pressure in heat exchanger tube is constantly reduced, and because intercommunicating pore 3-2-1 presence so that heat
Pressure distribution inside pipe is more and more uniform, therefore the area of intercommunicating pore need not be very big, is constantly reduced by setting, so that
So that in the case where ensureing the uniform pressure of inside heat pipe pressure, heat exchange area is increased by connecting the reduction of hole area,
So as to improve heat exchange efficiency.
It is preferred that, along the flow direction of fluid, the amplitude of the continuous reduction of area of the intercommunicating pore 3-2-1 constantly increases
Plus.It is also the changing rule for meeting flowing pressure by being arranged such, further while reduction flow resistance, improves heat exchange
Efficiency.By being arranged such, by being that experiment finds that 10% or so heat exchange efficiency can be improved, while resistance is kept not substantially
Become.
It is preferred that, along the flow direction of fluid, the distributed quantity of intercommunicating pore is fewer and fewer, further preferably, the company
The amplitude of the continuous reduction of number of openings 16 is continuously increased.
Principle is reduced by the Distribution Principle of above-mentioned quantity and area identical, area is reduced by distributed number less.
It is preferred that, intercommunicating pore 3-2-1's is shaped as circle.
It is preferred that, the inner fin 3-2 is multiple, and inner fin 3-2 stretches out from the central axis of pipe, with pipe
Inwall is connected, and the angle between the inner fin 3-2 is identical.It is identical by the angle between inner fin, heat exchanger tube can be caused
Internal flow distribution keeps uniform, and pressure distribution is also kept in balance accordingly.
It is preferred that, the inner fin 3-2 is 4, as shown in Figure 4.Angle between the inner fin is 90 °.
In actual experiment find, intercommunicating pore 3-2-1 area can not be too small, it is too small if can cause the increasing of flow resistance
Plus, and intercommunicating pore 3-2-1 minimum area is relevant with pipe caliber, and general is that caliber is bigger, then connects hole area just
What can be designed is smaller, and caliber is smaller, and it is bigger that intercommunicating pore 3-2-1 area can be designed, therefore intercommunicating pore 3-2-1 and pipe
The distance between caliber and its adjacent intercommunicating pore 3-2-1 must are fulfilled for certain requirement, otherwise may result in flow resistance excessive.
The inner fin is in the case of 4, the interior diameter of the pipe is D, the length of side B of the square intercommunicating pore, institute
The distance between intercommunicating pore adjacent on same fin is stated for S, following relation is met：
S/D*10>=a-b*LN(B/D*10)；
Wherein a, b are parameter, 13<a<14,11<b<12;LN is logarithmic function；
0.2<S/D<0.7；Preferably 0.35-0.63;
0.2<B/D<0.3
2.5<D<10m；
0.7<B<2.1m。
Wherein, S is equal to the distance between adjacent intercommunicating pore 3-2-1 centers.Left and right as shown in Figure 4,5 is adjacent and phase up and down
The distance between adjacent intercommunicating pore center.
Further preferably, 10<S<45mm.
It is preferred that, with B/D increase, described a, c increases, b reduces.
Preferably, S/D*10=- b*LN (B/D*10).
Now heat transfer effect reaches that most preferably, flow resistance meets requirement just.
If heat-exchanging tube bundle is arcuation, such as, as shown in figure 1, the arc length of the circular arc where described pipe is H, connect institute
The chord length of two-end-point of circular arc be S, then need to consider the brought resistance change of bending, then above-mentioned formula is changed into：
（S/D*10）*(S/H)c>=a-b*LN(B/D*10)；
Wherein c is parameter, 0.3<c<0.5;Further preferably, 0.38<c<0.41；Radian wherein where circular arc is 45-
75 degree, more preferably 50-60 degree.Above-mentioned degree is all angle.
Other parameter selections keep constant.
Preferably,（S/D*10）*(S/H)c>=a-b*LN (B/D*10), now heat transfer effect reaches most preferably, flows resistance
Power meets requirement just.
Preferably, as shown in Figure 4,5, multiple rows of intercommunicating pore 3-2-1, the multiple intercommunicating pore 3- are set on each inner fin
2-1 could be arranged to wrong row's structure.By mistake, row connects structure, can further improve heat exchange, reduces pressure.
As the application in being cooled down in nuclear reaction, as shown in figure 1, low flow resistance close-coupled Residual heat removal cooler shell side is interior
Shell 7 is that external diameter φ 18m are columnar structured, and shell 8 is also columnar structured for internal diameter φ 20m, between the two in the presence of about 1m one wide
Annular gap, interlayer bottom sets internal diameter φ 0.8m circular inlet port passages 6, and interlayer top is provided with internal diameter φ 0.8m circles and gone out
Mouth passage 9, interlayer is connected by intake channel 6 and exit passageway 9 with the space of low-temperature receiver 11, and cooling water is full of in interlayer.Low stream
Heating surface bank 3, inlet plenum 2 and the outlet chamber 4 of resistance close-coupled Residual heat removal cooler tube side are immersed in the cooling in interlayer
In water, the heat-transfer pipe that heating surface bank 3 is about 11m by 100 φ 20mm, average length is formed in circular arc arrangement, the He of inlet tube 1
The internal diameter φ 0.25m of outlet 5 pipe, is connected through inner casing 7 and with reactor core.
As shown in figure 1, in tube side, pyroreaction reactor coolant flows into inlet plenum 2 through inlet tube 1, then branches to 100
In heat-transfer pipe, water cooling is cooled down by shell side, the low-temp reaction reactor coolant after cooling imports outlet chamber 4, then is returned through outlet 5
Return reactor core, in the process heat-transfer pipe be heated elongation strain, but thermal stress because the circular arc arrangement of heating surface bank 3 be able to from
It is dynamic to eliminate.In shell side, cooling water is flowed up by reactor coolant heat temperature raising, and the top of low-temperature receiver 11 is discharged into through exit passageway 9,
And the low-temperature cooling water of the bottom of low-temperature receiver 11 also constantly sucks interlayer from intake channel 6, because Residual heat removal cooler shell side is logical
Road simple structure has the less feature of resistance, therefore forms the lasting natural circulation of larger flow.
Although the present invention is disclosed as above with preferred embodiment, the present invention is not limited to this.Any art technology
Personnel, without departing from the spirit and scope of the present invention, can make various changes or modifications, therefore protection scope of the present invention should
It is defined when by claim limited range.
Claims (3)
1. a kind of heat exchanger, the heat exchanger includes tube side side and shell side side, the tube side side include inlet tube, inlet plenum,
Heating surface bank, outlet chamber and outlet, hot fluid enter inlet plenum from inlet tube, pass sequentially through heating surface bank, outlet plenum
Room and outlet；The shell side side include intake channel, inner casing, shell and outlet chamber, cold fluid pass sequentially through intake channel,
Space and outlet chamber that inner casing and shell are limited, it is characterised in that the metallic rod that the heating surface bank outer wall stretches out, institute
Metal rod ends are stated for pointed structures, from direction from heating surface bank outer wall to the end of the metallic rod and the flowing side of cold fluid
To relative；
The metallic rod includes the sloping portion of connection heat-exchanging tube bundle and is connected with sloping portion and flat with heat-exchanging tube bundle axis
Capable parallel portion, pointed structures are arranged on the end of parallel portion；
Metallic rod is multiple, and the distribution density M of metallic rod is used as the function F apart from intake channel（S）, i.e. M=F (S), same
On root heat-exchanging tube bundle, F ' (S)>0, wherein F ' (S) is F（S）First order derivative；
F"(S)>(S) is F for 0, wherein F "（S）Second derivative.
2. heat exchanger as claimed in claim 1, it is characterised in that the included angle A of the metallic rod and heating surface bank outside wall surface is
30-60 degree.
3. heat exchanger as claimed in claim 1, it is characterised in that the distance between adjacent tube center of heat-exchanging tube bundle is
1.7-2.5 times of heat-exchanging tube bundle outer tube diameter, the pointed structures of the end of metallic rod are apart from the outer tube wall of heat-exchanging tube bundle apart from h
For 0.4-0.6 times of outer tube diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611052038.9A CN106767007B (en) | 2016-11-25 | 2016-11-25 | The heat exchanger of pointed structures is set outside a kind of pipe |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611052038.9A CN106767007B (en) | 2016-11-25 | 2016-11-25 | The heat exchanger of pointed structures is set outside a kind of pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106767007A CN106767007A (en) | 2017-05-31 |
| CN106767007B true CN106767007B (en) | 2017-09-15 |
Family
ID=58912943
Family Applications (1)
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109654918B (en) * | 2017-08-02 | 2021-02-19 | 青岛乾福圣耀商贸有限公司 | Gas-liquid two-phase flow heat exchange tube |
| CN108332179B (en) * | 2017-08-02 | 2019-04-19 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
| CN108332181B (en) * | 2017-08-02 | 2019-03-08 | 青岛金玉大商贸有限公司 | A kind of steam boiler |
| CN108332581B (en) * | 2017-08-02 | 2019-03-08 | 青岛金玉大商贸有限公司 | A kind of shell-and-tube heat exchanger |
| CN108332580B (en) * | 2017-08-02 | 2019-03-08 | 青岛金玉大商贸有限公司 | A kind of vehicle repair major flow tube shell type heat exchanger |
| CN109654917B (en) * | 2017-08-02 | 2021-07-23 | 彭小仙 | Vapor-liquid two-phase flow heat exchange tube |
| CN110822963B (en) * | 2017-08-03 | 2021-05-07 | 山东大学 | Design method for size of loop heat pipe fin |
| CN111238273B (en) * | 2017-08-03 | 2021-02-12 | 山东大学 | Rod-fin loop heat pipe with variable distance |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101182977A (en) * | 2007-12-11 | 2008-05-21 | 华南理工大学 | Inner chiasma spiral exterior three-dimensional diamond-type rib double-side intensify heat transfer pipe |
| CN101363694A (en) * | 2008-08-21 | 2009-02-11 | 西安石油大学 | Shell-pipe head exchanger by double helix flowing of fluid medium in or out of heat exchange tube |
| CN101532798A (en) * | 2009-03-31 | 2009-09-16 | 华北电力大学 | Reinforced heat transfer element of truncated cylindrical surface wing type vortex generator |
| CN102183008A (en) * | 2011-04-25 | 2011-09-14 | 山西晋城无烟煤矿业集团有限责任公司 | Coal economizer with high efficiency, corrosion resistance and hot dust erosion prevention |
| WO2012037745A1 (en) * | 2010-09-20 | 2012-03-29 | 北京华夏壹泰科技有限公司 | Self-cleaning enhanced heat transfer device used for heat exchange pipe and manufacturing method thereof |
| CN103673715A (en) * | 2013-12-19 | 2014-03-26 | 宁夏三新热超导技术有限公司 | Reinforced heat transferring element |
-
2016
- 2016-11-25 CN CN201611052038.9A patent/CN106767007B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101182977A (en) * | 2007-12-11 | 2008-05-21 | 华南理工大学 | Inner chiasma spiral exterior three-dimensional diamond-type rib double-side intensify heat transfer pipe |
| CN101363694A (en) * | 2008-08-21 | 2009-02-11 | 西安石油大学 | Shell-pipe head exchanger by double helix flowing of fluid medium in or out of heat exchange tube |
| CN101532798A (en) * | 2009-03-31 | 2009-09-16 | 华北电力大学 | Reinforced heat transfer element of truncated cylindrical surface wing type vortex generator |
| WO2012037745A1 (en) * | 2010-09-20 | 2012-03-29 | 北京华夏壹泰科技有限公司 | Self-cleaning enhanced heat transfer device used for heat exchange pipe and manufacturing method thereof |
| CN102183008A (en) * | 2011-04-25 | 2011-09-14 | 山西晋城无烟煤矿业集团有限责任公司 | Coal economizer with high efficiency, corrosion resistance and hot dust erosion prevention |
| CN103673715A (en) * | 2013-12-19 | 2014-03-26 | 宁夏三新热超导技术有限公司 | Reinforced heat transferring element |
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